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EP0098841B1 - Mecanisme de synchronisation - Google Patents

Mecanisme de synchronisation Download PDF

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Publication number
EP0098841B1
EP0098841B1 EP83900270A EP83900270A EP0098841B1 EP 0098841 B1 EP0098841 B1 EP 0098841B1 EP 83900270 A EP83900270 A EP 83900270A EP 83900270 A EP83900270 A EP 83900270A EP 0098841 B1 EP0098841 B1 EP 0098841B1
Authority
EP
European Patent Office
Prior art keywords
synchronizer
base plate
spring
sliding sleeve
synchronizer mechanism
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP83900270A
Other languages
German (de)
English (en)
Other versions
EP0098841A1 (fr
Inventor
Philip N. De Franco
Henry F. Jones, Jr.
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Massey Ferguson Services NV
Original Assignee
Massey Ferguson Services NV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Massey Ferguson Services NV filed Critical Massey Ferguson Services NV
Publication of EP0098841A1 publication Critical patent/EP0098841A1/fr
Application granted granted Critical
Publication of EP0098841B1 publication Critical patent/EP0098841B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F16D23/0606—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation the blocking mechanism comprising an axially-extending shouldered pin passing through a hole in a radial wall

Definitions

  • the present invention relates generally to a synchronizer mechanism, and more particularly to a synchronizer of the type employing blocking pins.
  • the synchronizer assembly of this invention is usable with a constant mesh gear transmission of the shift collar type.
  • a transmission customarily includes parallel shafts on which are mounted intermeshing gears.
  • one of the intermeshing gears is fixed to the shaft on which it is mounted while the other intermeshing gear is journalled about its associated shaft.
  • the journalled gear is coupled to the associated shaft by means of a shift collar or sliding sleeve which is laterally shifted to cause internal splines on the sliding sleeve to engage both the external splines on a drive hub and clutch teeth on the gear.
  • a synchronizer is employed to insure that either the sliding sleeve or gear is accelerated (either positively or negatively) to the same speed as the other.
  • the location of the synchronizer within the transmission will determine whether the gear or the sliding sleeve is accelerated to match the speed of the other. In the following, it will be assumed that the sliding sleeve will be accelerated.
  • the synchronizer includes a clutch surface which is capable of engaging a corresponding clutch surface carried by the gear.
  • the present invention relates to a synchronizer assembly of the type generally referred to as a blocking pin synchronizer.
  • This form of synchronizer is generally well known in the art, and representative designs are shown in US-A-3,078,975, US-A-3,910,390, and US-A--4,018,319. All of these designs have the following in common:
  • the gear assemblies which are to be synchronized are journalled about a shaft, and include clutch teeth rotatable with the gear and a clutch member having a conical clutch surface.
  • Each of the synchronizers include a shift collar or sliding sleeve having a plurality of apertures.
  • two additional clutch members having conical clutch surfaces cooperable with the clutch surfaces on the gear assemblies are coupled together by blocker pins which pass through certain of the apertures in the sliding sleeve.
  • Spring assemblies which govern the synchronizer action also pass through other certain apertures in the sliding sleeve and are interconnected with cones.
  • the spring assemblies of the prior art include two semi-cylindrical members having springs disposed between them. While these prior art designs are generally satisfactory, it is desirable that a synchronizer be provided having a higher capacity within a given volume than the prior art, which synchronizer will have an acceptable service life.
  • the known prior art designs utilize close tolerance components which are difficult to machine.
  • a synchronizer mechanism capable of selectively connecting either of two gears to a shaft upon which they are rotatably mounted, the synchronizer mechanism comprising a sliding sleeve interconnected with said shaft for rotation therewith, the sliding sleeve having a plurality of apertures, a pair of synchronizer cones disposed on opposite sides of the sliding sleeve and rigidly joined together by at least two blocker pins extending through certain of said apertures, and at least two spring assemblies disposed between the synchronizer cones and extending through other of said apertures, each of said spring assemblies comprising an elongated housing which is split longitudinally into two parts with said parts biased apart by spring means into contact with the sleeve and with the ends of the spring assembly received in opposed recesses in the cones, the synchronizer mechanism being characterised in that each spring assembly housing is generally rectangular in cross-section in planes at right angles to the direction of sliding of the sleeve and comprises a generally rectangular cross-
  • the spring means may comprise a pair of elongated opposed leaf springs whose ends are in contact with each other and whose mid portions are in contact with an intermediate surface of either the base plate or the main housing part.
  • the main housing part preferably has a base portion and opposed sides extending generally at right angles away from the base portion with the associated base plate and spring means disposed between the opposed sides.
  • Each of the sides of the main housing part may be provided with a slot and the associated spring means and base plate may have outwardly extending tabs received within the slots.
  • the opposed recesses are preferably provided with an upper wall surface extending in a plane generally at right angles to the diameter of the associated synchronizer cone, and surfaces of the base plate are biased into contact with associated upper wall surfaces whereby rotational movement of the spring assembly is prevented.
  • a transmission shaft 10 is illustrated, a pair of gear assemblies indicated generally at 12 and 14 being rotatably mounted thereon.
  • each of these gear assemblies is in constant mesh with another gear assembly (not shown) which is fixed to a further shaft parallel to the first shaft 10.
  • Each of the gear assemblies 12, 14 is journalled on the shaft 10 by bearing sleeves 16, 18, respectively, and each gear assembly includes gear teeth 20 and clutch teeth 22.
  • Also mounted on each of the gear assemblies 12 and 14 is a synchronizer ring 24 having an internal conical surface 26 disposed radially outwardly of the clutch teeth 22.
  • the synchronizer ring is preferably secured to the adjacent portion of the associated gear assembly by means of electron beam welding to increase heat transfer characteristics.
  • a drive hub 28 Disposed between the gear assemblies 12, 14 is a drive hub 28, which hub is provided with internal splines 30 in driving relationship with external splines 32 on the shaft 10.
  • the hub 28 is also provided with external splines 34.
  • Mounted on the drive hub is an axially movable shift collar or sliding sleeve, indicated generally at 36, this sliding sleeve being provided with internal splines 38 which are engaged by the external splines 34 on the drive hub 28.
  • the clutch teeth 22 can be placed in alignment with the external splines 34 on the hub, and the sliding sleeve 36 can be moved from a neutral position, such as shown in Fig. 1, to an engaged position wherein the internal splines 38 engage both the external splines 34 and the clutch teeth 22.
  • the clutch teeth 22 and external splines 34 are provided with chamfered ends to assist engagement.
  • the synchronizer of this invention includes, in addition to the sliding sleeve 36, and synchronizer rings 24, three cylindrical blocking pins 40 and a pair of annular synchronizer cones 42, each provided with an external conical surface 43 engageable with the corresponding internal conical surfaces 26 of the rings 24.
  • Each of the blocking pins includes reduced end portions 44, a reduced central portion 46, and a pair of intermediate portions 48 disposed between the central portion 46 and the end portions 44.
  • Each of the reduced end portions is countersunk as at 50 to facilitate the staking of the blocking pin 40 to the associated synchronizer cone 42, the reduced end portion being disposed within an aperture within the synchronizer cone 42, the shoulder between the reduced end portion 44 and the intermediate portion 48 abutting against a face 52 of the synchronizer cone 42.
  • Chamfered portions 54 extend between the reduced central portion 46 and the intermediate portions 48.
  • Each of the cylindrical blocking pins 40 passes through a cylindrical aperture 56 in an outwardly extending flange portion 58 of the sliding sleeve 36, a chamfered portion 60 being formed in the flange 58 adjacent the aperture 56.
  • the synchronizer additionally includes three spring assemblies 62, each spring assembly including a housing in the form of a main housing part 64 of generally rectangular cross-section in planes at right angles to the direction of sliding of sleeve 36 and a base plate 66 with a pair of opposed leaf springs 68 therebetween.
  • This structure is best illustrated in Fig. 3.
  • the flange or disc portion 58 of the sliding sleeve is further provided with generally rectangular shaped apertures 70 which receive the spring assemblies 62.
  • a protrusion 72 extends radially outwardly into each of the rectangular apertures 70.
  • Each of the spring housings is a width W just slightly less than the distance D (Fig. 4) between the facing surfaces 52 of the synchronizer cone 42.
  • Each main spring housing part 64 includes a base portion 74 having radially inner and outer generally parallel planar surfaces 76, 78, respectively.
  • the radial inner surface 76 is provided with a transversely extending groove 80 which receives the protrusion 72 when the parts are in the neutral position as illustrated in Fig. 1.
  • the spring housing further includes opposed parallel sides 82 which extend radially outwardly from the base portion at generally right angles thereto. Each of the sides 82 is provided with an intermediate slot 84.
  • the elongated base plate 66 is of a length L greater than distance D, the ends 86 being received in relatively narrow slots or recesses 88 formed in the synchronizer cones 42.
  • An intermediate portion 90 of the base plate 66 is provided with outwardly extending tabs 92 which are received within the slots 84 for radial sliding movement.
  • each of the slots or recesses 88 has an upper wall surface (no number) lying in a plane generally at right angles to the diameter of the cone, this surface being engaged by the corresponding surface of the end 86 of the base plate 66.
  • Each of the leaf springs 68 is of the length similar to that of the base plate 66, each spring leaf being arched between flattened end portions 94, the intermediate arched portion 96 being provided with outwardly extending tabs 98 which are also received within the slots 84 for radial sliding movement. It should be obvious that the tabs 92 and 98 maintain the base plate and the leaf springs in a relatively centred position. When the parts are in the neutral position shown in Fig. 1 the springs 68 will hold the spring housing and base plate apart to maintain the outer surface of the ends 86 of the base plate in contact with the radially outer surface of the slots or recesses 88, and also to maintain the groove 80 in the spring housing part 64 in contact with the protrusion 72. If the normal force of the springs 68 is not great enough, shims (not shown) may be inserted between one of the springs and the base plate 66.
  • the shift force exerted by the sliding sleeve 36 moves the blocking pins 40 aside so that the spline 38 on sliding sleeve can engage the clutch teeth 22 on the gear assembly.
  • the axial force exerted on the chamfer 54 of the blocking pins by the chamfered portion 60 of the sliding sleeve produces a push-through torque which is opposed to the index torque.
  • the blocking action continues until the index torque value drops below the push-through torque value, which occurs when synchronization is substantially achieved and the acceleration portion of the index torque is substantially reduced.
  • the synchronizer cones 42 and the blocking pins 40 rotate relative to the sliding sleeve which permits the sliding sleeve to move over the blocking pins while compressing the leaf springs 68 within the spring housing part 64. This occurs when the protrusion 72 rides out of the groove 80 forcing the housing part 64 upwardly towards the base plate 66 thereby compressing the spring 68. It is essential that the initial rotation of the synchronizer cone 42 and the blocking pins 40 occur before the springs 68 are compressed, thus the mangitude of the required axial force (to produce index torque) must be less than the force of the springs so that the desired indexing rotation occurs and not deflection of the springs 68.
  • the springs 68 be compressed so that the protrusion 72 can move out of the groove 80 in the spring housing 64, and the sliding sleeve 36 can move to engage the clutch teeth 22 with the internal splines 38.
  • the present design utilizes leaf springs 68 which act on flat surfaces, namely the radial outer planar surface 78 of the spring housing 64 and the radially inner surface of the base plate 66.
  • This design assures that only bending stresses (compression or tension) are present, and not bending plus torsion as in other existing designs.
  • the advantages of removing the torsional loading includes an increased spring service life, a more predictable load for the indexing operation, and a more reliable operation.
  • the present design achieves maximum use of springs in a minimum package volume leading to a synchronizer design of high torque capacity in a minimum envelope size.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Claims (7)

1. Mécanisme de synchronisation capable d'accoupler sélectivement l'un ou l'autre de deux engrenages (12, 14) à un arbre (10) sur lequel ils sont montés rotatifs, le mécanisme de synchronisation comprenant un manchon coulissant (36) interconnecté avec l'arbre pour tourner avec celui-ci, le manchon coulissant comportant une pluralité de trous ou orifices (56, 70), deux cônes de synchronisation (42) disposés sur des côtés opposés du manchon coulissant et reliés rigidement l'un à l'autre par au moins deux broches de blocage (40) qui traversent certains (56) desdits orifices, et au moins deux sous-ensembles à ressort (62)disposés entre les cônes de synchronisation et traversant d'autres (70) desdits orifices, chacun de ces sous-ensembles à ressort comprenant un boîtier allongé (64, 66) qui est divisé longitudinalement en deux parties, lesdites parties étant écartées l'une de l'autre par des moyens à ressort (68) en contact avec le manchon, et les extrémités du sous-ensemble à ressort étant reçues dans des logements opposés (88) ménagés dans les cônes, le mécanisme de synchronisation étant caractérisé en ce que chaque boîtier (64, 66) de sous-ensemble à ressort est sensiblement rectangulaire en section transversale dans des plans perpendiculaires à la direction de coulissement du manchon (36) et comprend une partie principale de boîtier (64), à section transversale sensiblement rectangulaire, et une plaque de base allongée (66), les dits moyens à ressort (68) étant disposés entre la plaque de base et la partie principale du boîtier, et en ce que les logements (88) prévus dans les cônes de synchronisation (42) ont une configuration telle qu'ils reçoivent les extrémités (86) de la plaque de base (66) pour empêcher la rotation du sous-ensemble à ressort.
2. Mécanisme de synchronisation suivant la revendication 1, caractérisé en ce que les dits moyens à ressort comprennent deux ressorts à lame opposés allongés (68) dont les extrémités (94) sont en contact l'une avec l'autre et dont les parties intermédiaires (96) sont en contact avec une surface intermédiaire de la plaque de base (66) ou de la partie principale du boîtier (64).
3. Mécanisme de synchronisation suivant la revendication 1 ou la revendication 2, caractérisé en ce que chacun des logements opposés (88) comporte une surface de paroi supérieure s'étendant dans un plan sensiblement perpendiculaire au diamètre du cône de synchronisation associé (42), et les surfaces (86) de la plaque de base (66) sont poussées en contact avec les surfaces de paroi supérieure associées, de sorte qu'un mouvement de rotation du sous-ensemble à ressort (62) est empêché.
4. Mécanisme de synchronisation suivant l'une quelconque des revendications 1 à 3, caractérisé en ce que le manchon coulissant (36) comporte une pluralité de bossages (72) dirigés radialement vers l'extérieur, et en ce que chacune desdites parties principales de boîtier (64) comporte une gorge (80), chacun des bossages s'engageant dans une gorge associée lorsque le mécanisme de synchronisation est dans une position neutre.
5. Mécanisme de synchronisation suivant l'une quelconque des revendications 1 à 4, caractérisé en ce que chaque partie principale de boîtier (64) comprend une partie de base (74) et des côtés opposés (82) qui partent sensiblement perpendiculairement de la partie de base, la plaque de base associée (66) et les moyens à ressort (68) étant disposés entre lesdits côtés opposés (82).
6. Mécanisme de synchronisation suivant l'une quelconque des revendications 1 à 5, caractérisé en ce que chacune desdites plaques de base allongées (66) présente des surfaces planes parallèles opposées dont l'une est en contact avec lesdits moyens à ressort (68).
7. Mécanisme de synchronisation suivant la revendication 5 ou 6, caractérisé en ce que chacun des côtés (82) de la partie principale de boîtier (64) comporte une rainure (84), et les moyens à ressort associés (68) et la plaque de base (66) comportent des languettes (92, 98) dirigées vers l'extérieur qui sont reçues dans les rainures.
EP83900270A 1982-01-20 1983-01-07 Mecanisme de synchronisation Expired EP0098841B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/341,034 US4478321A (en) 1982-01-20 1982-01-20 Synchronizer mechanism
US341034 1982-01-20

Publications (2)

Publication Number Publication Date
EP0098841A1 EP0098841A1 (fr) 1984-01-25
EP0098841B1 true EP0098841B1 (fr) 1987-04-15

Family

ID=23335992

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83900270A Expired EP0098841B1 (fr) 1982-01-20 1983-01-07 Mecanisme de synchronisation

Country Status (9)

Country Link
US (1) US4478321A (fr)
EP (1) EP0098841B1 (fr)
JP (1) JPS59500107A (fr)
CA (1) CA1196212A (fr)
DE (1) DE3370981D1 (fr)
ES (1) ES519076A0 (fr)
IT (1) IT1161852B (fr)
WO (1) WO1983002485A1 (fr)
ZA (1) ZA829333B (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5097930A (en) * 1990-12-24 1992-03-24 Eaton Corporation Pre-energizer for a synchronizer
US5141087A (en) * 1990-12-24 1992-08-25 Eaton Corporation Self-energizing synchronizer
US5161423A (en) * 1990-12-24 1992-11-10 Eaton Corporation Self-energizing synchronizer for equalizing shift time and effort of a multi-ratio transmission
USRE35796E (en) * 1990-12-24 1998-05-19 Eaton Corporation Self-energizing synchronizer
US5078244A (en) * 1990-12-24 1992-01-07 Eaton Corporation Self-energizing synchronizer
US5269400A (en) * 1992-10-20 1993-12-14 Borg-Warner Automotive, Inc. Transmission synchronizer
US5339936A (en) * 1993-05-24 1994-08-23 Eaton Corporation Synchronizer pre-energizer spring system
US5738195A (en) * 1996-09-16 1998-04-14 Eaton Corporation Pin-type synchronizer
US6102180A (en) * 1996-09-16 2000-08-15 Eaton Corporation Pin-type synchronizer
US5769198A (en) * 1996-09-16 1998-06-23 Eaton Corporation Pin-type synchronizer
US20050262957A1 (en) * 2004-05-25 2005-12-01 Razzacki Syed T Synchronizer design
CN102518694A (zh) * 2012-01-01 2012-06-27 赵孝民 一种汽车同步器
CN108253036B (zh) * 2018-02-11 2023-06-16 十堰同创传动技术有限公司 卡爪式同步器组合滑块
CN108194531B (zh) * 2018-02-11 2023-06-16 十堰同创传动技术有限公司 卡扣式同步器组合滑块

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2221893A (en) * 1937-08-25 1940-11-19 Borg Warner Transmission synchronizer
US2179568A (en) * 1937-08-25 1939-11-14 Borg Warner Transmission synchronizer
US2814373A (en) * 1952-08-21 1957-11-26 Rockwell Spring & Axle Co Synchronizer
DE902566C (de) * 1952-10-01 1954-01-25 Volkswagenwerk G M B H Sperrsynchrongetriebe mit Sperrstuecken
US3078975A (en) * 1961-06-19 1963-02-26 Clark Equipment Co Synchronizer
FR1385860A (fr) * 1964-03-03 1965-01-15 Smith & Sons Ltd S Perfectionnements aux mécanismes à engrènement synchronisé, notamment pour changements de vitesses
US3529484A (en) * 1967-08-12 1970-09-22 Toyota Motor Co Ltd Synchronizing device
GB1280299A (en) * 1969-03-06 1972-07-05 Brown Tractors Ltd Improvements in synchronizing mechanisms for power transmissions
DE2315388A1 (de) * 1973-03-28 1974-10-10 Hurth Masch Zahnrad Carl Synchronisiereinrichtung fuer zahnkupplungen in zahnradwechselgetrieben
US4018319A (en) * 1976-01-28 1977-04-19 Clark Equipment Company Synchronizer assembly

Also Published As

Publication number Publication date
JPS59500107A (ja) 1984-01-19
ES8401587A1 (es) 1983-12-16
WO1983002485A1 (fr) 1983-07-21
ZA829333B (en) 1983-09-28
CA1196212A (fr) 1985-11-05
IT1161852B (it) 1987-03-18
DE3370981D1 (en) 1987-05-21
ES519076A0 (es) 1983-12-16
EP0098841A1 (fr) 1984-01-25
US4478321A (en) 1984-10-23
IT8319180A0 (it) 1983-01-19

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